JP2010121644A - Flexible coupling structure and marine thruster device having the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a flexible coupling structure without generating vibration even if the total length is long. <P>SOLUTION: This metallic spring type or rubber type coupling structure 15 is provided for connecting a driving shaft 13 and a driven shaft 14. Radial spherical bearings 42 and 42 are incorporated so that its rotational center is positioned in a position of the deflection centers O and O of deflection materials 17 and 19 composed of a metallic spring or rubber, by interposing between driving shaft side rotary shaft members 16 and 18 and driven shaft side rotary shaft members 18 and 20. The driving shaft side rotary shaft members 16 and 18 or the driven shaft side rotary shaft members 18 and 20 are supported by the radial spherical bearings 42 sand 42 so that the driving shaft side rotary shaft members 16 and 18 can be relatively inclined to the driven shaft side rotary shaft members 18 and 20 on the basis of the deflection centers O and O. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a flexible coupling structure that connects a drive shaft and a driven shaft and transmits the rotation of the drive shaft to the driven shaft, and a marine thruster apparatus including the flexible coupling structure.

  Conventionally, in a land machine or a marine machine, a flexible coupling may be employed in a structure for transmitting the power of a prime mover to a driven machine (see, for example, Patent Document 1). As a result, even if the axis of the drive shaft provided on the prime mover deviates from the axis of the driven shaft provided on the driven machine when both machines are installed, this can be absorbed in a short time without using nerves for installation accuracy. Installation work can be completed. In particular, in a ship, the distance between a prime mover and a driven machine such as a thruster is several tens of meters, and a slight deformation of a reference base (hull) for machine installation may cause a shift in the axis. In order to easily cope with such a situation, a flexible coupling is frequently used. In addition to gear-type shaft couplings (hereinafter referred to as “gear couplings”), metal spring shaft couplings (hereinafter referred to as “metal spring type flexible couplings”) and rubber shaft couplings (hereinafter referred to as “rubbers”) Is called "type flexible coupling").

  FIG. 16 is a cross-sectional view of a metal spring type flexible coupling 1 shown as an example of a conventional flexible coupling. The flexible coupling 1 shown in FIG. 16 includes a drive shaft side hub 3 connected to the drive shaft 2, a driven shaft side hub 5 connected to the driven shaft 4, a spacer 6 interposed between the hubs 3 and 5, and Two sets of disk elements 7 and 7 interposed between the hubs 3 and 5 and the spacer 6 are provided, and the structure is simple. Further, the gear coupling is advantageous in that it does not require the supply of operating lubricant and is not affected by backlash. Each disk element 7, 7 is formed by laminating a plurality of disk-shaped metal leaf springs, and can be bent and deformed around a bending center O. Due to this bending, both shafts 2 and 4 can be displaced in parallel in the radial direction, and even though the axes of these shafts 2 and 4 are parallel, they can be allowed even if they are not on the same straight line. Further, both the shafts 2 and 4 can be tilted and displaced (angular displacement), and this is allowed even if the axes of the shafts 2 and 4 do not intersect with each other and are not on the same straight line. Furthermore, a relative displacement combining these two can be realized. If the flexible coupling 1 is incorporated in this way, the power from the drive shaft 2 can be smoothly and reliably transmitted to the driven shaft 4 while following various relative displacements between the shafts 2 and 4.

  However, if the prime mover and the driven machine are separated, the intermediate spacer 6 needs to be long. If the spacer 6 is short, the accuracy of its rotational balance is low, and even if the unbalance is large, it is difficult to cause a problem. However, the longer the dimension, the greater the weight and the unbalance, so that the unbalance force increases. Lateral vibration is likely to occur during rotation due to the action of the balancing moment. Since the unbalance force is proportional to the square of the rotational speed, a machine that operates at a medium rotational speed of several hundreds of revolutions or a high rotational speed of several hundreds of revolutions, In comparison, the effect of vibration is increased.

FIG. 17 is a front view of a conventional marine thruster apparatus including the flexible coupling 1 shown in FIG. If the prime mover 8 that can be operated at medium and high speeds and the thruster 9 that is the driven machine are separated from each other as in the marine thruster device shown in FIG. In this case, a structure in which the spacer is simply extended cannot be adopted. Therefore, a set of flexible couplings 1 and 1 are attached to the prime mover 8 side and the thruster 9 side, respectively, intermediate shafts 10 and 10 are attached therebetween, and an appropriate number of intermediate bearings 11 for supporting the intermediate shafts 10 and 10 are provided. Provided.
JP 2000-2261 A

  However, as shown in FIG. 17, when the prime mover and the driven thruster are separated in the vertical direction and the flexible coupling 1 is of the vertical axis type, the wall extending vertically to fix the intermediate bearing 11 is used. The part 12 needs to be installed. The manufacture of the marine thruster including the installation of the wall portion 12 requires a great amount of cost, man-hours, and time, so this improvement is strongly demanded. Similarly, when the flexible coupling is a horizontal shaft type, it is necessary to provide an intermediate bearing to suppress the lateral vibration of the intermediate shaft, and to install a horizontally extending wall or floor to fix the intermediate bearing. May occur.

  Therefore, an object of the present invention is to provide a flexible coupling structure in which vibration does not occur even when the entire length is long, and a marine thruster apparatus including the flexible coupling structure.

  The present invention has been made in view of the above-mentioned circumstances, and the flexible coupling structure according to the present invention is a metal spring type or rubber type coupling structure that connects a drive shaft and a driven shaft, and rotates on the drive shaft side. A radial spherical bearing is installed so that the center of rotation is located at the center of bending of a bending material made of a metal spring or rubber interposed between the shaft member and the rotating shaft member on the driven shaft side. The rotating shaft member or the rotating shaft member on the driven shaft side is supported by the radial spherical bearing, and the rotating shaft member on the driving shaft side is relative to the rotating shaft member on the driven shaft side with respect to the bending center. It is characterized by being able to incline.

  As a result, even if an unbalanced force is generated, the load that accompanies this is supported by the radial spherical bearing. In this way, since the lateral runout load during rotation is supported, the occurrence of lateral vibration can be suppressed even if the overall length is long or the drive shaft is rotating at a medium to high speed. Since the rotational center of this radial spherical bearing coincides with the bending center of the bending material, it is possible to perform relative parallel displacement and tilt displacement while receiving an unbalanced force.

  A bearing support portion for mounting the radial spherical bearing is fixed to one of the rotating shaft member on the drive shaft side and the rotating shaft member on the driven shaft side, and is supported by the radial spherical bearing. The support shaft may be fixed to the other side. Thereby, the support of the lateral run-out load using the radial spherical bearing is realized. Note that it is possible to appropriately select which rotating shaft member the bearing support portion and the bearing support shaft are fixed to depending on the specification.

  The rotary shaft member on the drive shaft side or the rotary shaft member on the driven shaft side includes a main body portion and a split end portion to which the bearing support portion or the bearing support shaft is fixed while being combined with the bending material. And the main body and the split end may be integrated by fastening with a joint bolt including a reamer bolt. As a result, in one of the rotating shaft members on the driving shaft side and the rotating shaft member on the driven shaft side, only the end portion on the side combined with the bending material and the radial spherical bearing can be separated. For this reason, it is possible to perform an operation to confirm whether or not the flexible coupling structure is properly assembled in a stage before the split end portion is fastened to the main body portion and the one rotating shaft member is integrated. it can.

  The metal spring type or rubber type flexible coupling structure may be a vertical shaft type, and the radial spherical bearing may have a large load capacity, and may be capable of supporting loads in the radial direction and the thrust direction. As a result, the radial spherical bearing also supports the load in the thrust direction, and the structure can be simplified.

  The metal spring-type or rubber-type flexible coupling structure is a vertical shaft type, and a thrust spherical bearing is incorporated in the position of the bending center of the bending material so that the rotation center is positioned, and the rotating shaft member on the drive shaft side Alternatively, the rotary shaft member on the driven shaft side may be supported by the radial spherical bearing and the thrust spherical bearing. Thereby, since the rotation center of a thrust spherical bearing is in agreement with the bending center of a bending material, relative parallel displacement and inclination displacement can be performed, receiving unbalanced force. Further, the weight of the flexible coupling structure can be received by the thrust spherical bearing.

  A bearing support shaft for mounting the thrust spherical bearing is fixed to any one of the rotating shaft member on the drive shaft side and the rotating shaft member on the driven shaft side, and is supported by the thrust spherical bearing. May be fixed to the other side. Thereby, support of the load of the thrust direction using a thrust spherical bearing is realized. Note that it is possible to appropriately select which rotating shaft member the bearing support portion and the bearing support shaft are fixed to depending on the specification.

  The radial spherical bearing may be mounted on a bearing support portion for mounting the thrust spherical bearing, and a tip end portion of a bearing support shaft supported by the radial spherical bearing may be supported by the thrust spherical bearing. Thus, the bearing support portion and the bearing support shaft are shared between the thrust spherical bearing and the radial spherical bearing. For this reason, the structure can be simplified, and two unitized bearings can be easily attached and detached simultaneously.

  A spacer interposed between the rotating shaft member of the driving side shaft and the rotating shaft member of the driven side shaft; the spacer serving as a rotating shaft member on the driven shaft side with respect to the rotating shaft member on the driving shaft side; Functions as a rotating shaft member on the driven shaft side with respect to the rotating shaft member on the driven shaft side, and the first bending material is interposed between the rotating shaft member on the driving shaft side and the spacer. The first radial spherical bearing incorporated so that the center of rotation is located at the position of the center of deflection of the first deflecting material is supported by the rotating shaft member or the spacer on the drive shaft side, and the spacer and the driven The second radial spherical bearing is assembled so that the second bending material is interposed between the rotation shaft members on the shaft side, and the rotation center is located at the position of the bending center of the second bending material. Supported by the rotating shaft member on the spacer or driven shaft side. , The thrust spherical bearing may be incorporated into either one of said first radial spherical bearing and the second radial spherical bearing. Thus, for example, when the thrust spherical bearing is incorporated in the second radial spherical bearing when the drive shaft is disposed above the driven shaft, the weight of the spacer is received by the thrust spherical bearing, and further the weight is received by the driven shaft. be able to.

  The radial spherical bearing may be a spherical plain bearing or a spherical rolling bearing, and the thrust spherical bearing may be a spherical plain bearing or a spherical rolling bearing. Since spherical plain bearings and spherical rolling bearings are general-purpose products that can be mass-produced, the adoption of these can avoid the cost required for the production and maintenance of the flexible coupling structure. The bending material may be a disk-shaped leaf spring, a lattice-shaped leaf spring, or a tire-shaped rubber.

  A marine thruster apparatus according to the present invention includes the flexible coupling structure described above, and rotation generated in the drive shaft provided in the prime mover is transmitted to the driven shaft provided in the thruster via the flexible coupling structure. It is characterized by being composed.

  Thereby, as described above, it is possible to suppress the occurrence of lateral vibration in the flexible coupling structure, and it is not necessary to provide an intermediate bearing in the marine thruster device or to install a wall portion or a floor portion for fixing the intermediate bearing.

  Thus, according to the present invention, even if the overall length is long, the occurrence of lateral vibration of the flexible coupling structure can be suppressed, and it is necessary to install a wall portion and a floor portion for fixing the intermediate bearing that supports the flexible coupling structure. Disappear. For this reason, it is possible to reduce the cost, man-hours and time required for the production of the flexible coupling structure and the marine thruster equipped with the flexible coupling structure, and the space reserved for installing the wall portion and the floor portion is used for other purposes. Can be used effectively.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

[First Embodiment]
FIG. 1 is a cross-sectional view of a horizontal axis type flexible coupling structure according to a first embodiment of the present invention. The flexible coupling structure 15 shown in FIG. 1 connects the drive shaft 13 and the driven shaft 14 and transmits the rotation of the drive shaft 13 to the driven shaft 14. They are arranged so that they are oriented almost horizontally. When this flexible coupling structure 15 is applied to a marine thruster device, the drive shaft 13 is connected to a motor (not shown) such as an electric motor or a diesel engine to function as an output shaft of the motor, and the driven shaft 14 is driven. It is connected to a thruster (not shown) as a motive and functions as an input shaft of the thruster. When the prime mover is operated, the drive shaft 13 is rotated at a rotational speed of, for example, several hundreds of revolutions per minute or more, and the rotation is transmitted to the driven shaft 14 via the flexible coupling structure 15, thereby propelling the thruster. (Not shown) is driven to rotate. In the marine thruster device, the prime mover and the thruster tend to be arranged apart from each other (for example, 10 meters). Accordingly, the total length of the flexible coupling structure 15 interposed therebetween is relatively long.

  The flexible coupling structure 15 mainly includes a drive shaft side hub 16, a first disk element 17, a spacer 18, a second disk element 19, and a driven shaft side hub 20 in order from the left side. Are transmitted in this order. Increasing the axial length of the structure 15 can be dealt with by increasing the axial length of the intermediate spacer 18. According to the present invention, since the occurrence of lateral vibration can be suppressed as will be described later, the spacer 18 is not supported by a dedicated intermediate bearing and rotates to the prime mover and the driven machine via the drive shaft 13 and the driven shaft 14. It is in a state of being supported as possible.

  The long spacer 18 is composed of a total of three parts, that is, a main body portion 21 on the center side in the axial direction and divided end portions 22 and 23 on both end sides. The integrated spacer 18 is configured by fastening with a plurality of joint bolts such as a reamer bolt 24. In this integrated state, the axial centers 18A of the three parts are located on the same straight line. An annular flange portion 25 is formed on the left end portion of the left split end portion 22, that is, the end portion on the side facing the drive shaft side hub 16 in the axial direction, protruding radially outward from the outer peripheral surface thereof. A similar flange portion 26 is formed at the right split end portion 23, and this flange portion 26 faces the driven shaft side hub 20.

  The drive shaft side hub 16 is formed in a cylindrical shape that is open at both ends, and the right end portion of the drive shaft 13 is fitted into the drive shaft side hub 16. The drive shaft side hub 16 is fastened to the drive shaft 13 by a key 27, and rotates integrally with the drive shaft 13 in a state where the shaft center thereof coincides with the shaft center 13A of the drive shaft 13. An annular flange portion 28 that protrudes radially outward from the outer peripheral surface is formed at the right end portion of the drive shaft side hub 16, that is, the end portion facing the spacer 18 in the axial direction. Similarly to this, the left end portion of the driven shaft 14 is fitted into the driven shaft side hub 20 and fastened to the driven shaft 14 with a key 29, and its axis is aligned with the axis 14 A of the driven shaft 14. In this state, it rotates integrally with the driven shaft 14. A flange portion 30 similar to that described above is also formed at the left end portion of the driven shaft side hub 20, that is, the end portion on the side facing the spacer 18 in the axial direction. The shaft centers of the drive shaft side hub 16 and the driven shaft side hub 20 are described with reference numerals 13A and 14A for convenience.

  The first disk element 17 is interposed between the flange portion 28 of the drive shaft side hub 16 and the flange portion 25 of the left split end portion 22, and can transmit the rotation of the drive shaft side hub 16 to the spacer 18. . The second disk element 19 is interposed between the flange portion 26 of the right split end portion 23 and the flange portion 30 of the driven shaft side hub 20, and can transmit the rotation of the spacer 18 to the driven side shaft hub 20. . In this way, the spacer 18 that forms the intermediate portion of the flexible coupling structure 15 functions as a driven shaft side rotating shaft member to which rotation is transmitted from the driving shaft side hub 16 to the driving shaft side hub 16. The shaft-side hub 20 functions as a drive shaft-side rotation shaft member that transmits rotation to the driven shaft-side hub 20.

  Although the first and second disk elements 17 and 19 are arranged symmetrically in the axial direction, the structure of each other is the same. For this reason, here, the first disk element 17 will be mainly described as a representative of the two, and the second disk element 19 will be denoted by the same reference numeral, and redundant description will be omitted.

  FIG. 2 is an exploded perspective view of the flexible coupling structure 15 shown in FIG. In FIG. 2, illustration of a configuration relating to a radial spherical bearing described later is omitted. As shown in FIGS. 1 and 2, the first disk element 17 is configured by stacking a plurality of metal plate springs 31 in the axial direction. Each leaf spring 31 is formed in a donut disk shape having a circular through-hole at the center thereof, and in an overlapped state with an even number (6 in this embodiment) of bolts 32 and nuts 33. Fastened to the flange portions 28 and 25. For the insertion of the bolt 32, an even number (six in this embodiment) of bolt holes 34 to 36 communicating with each other in the axial direction are formed through the leaf spring 31 and the flange portions 28 and 25. The same number (three in the present embodiment) of small-diameter bolt holes 35 and large-diameter bolt holes 36 are alternately arranged in the circumferential direction on the flange portion 28 of the drive shaft side hub 16. Similarly, a small-diameter bolt hole 35 and a large-diameter bolt hole 36 are formed in the flange portion 25 of the left split end portion 22. The outer contour of the leaf spring 31 has a hexagonal shape according to the number of the bolt holes 34 according to the illustration in FIG. 2, but may have another polygonal shape or a circular shape.

  Returning to FIG. 1, each small-diameter bolt hole 35 of the drive shaft side hub 16 communicates with the large diameter bolt hole 36 of the left split end portion 22 via the bolt hole 34 of the leaf spring 31. The large-diameter bolt hole 36 is communicated with the small-diameter bolt hole 35 of the flange portion 25 of the left split end portion 22 through the bolt hole 34 of the leaf spring 31. Each bolt 32 is inserted through the small diameter bolt hole 35, and is inserted through the bolt hole 34 of each leaf spring 31 into the large diameter bolt hole 36. As a result, the first disk element 17 is sandwiched between the two flange portions 28 and 25, but washers 39 and 39 are interposed between the first disk element 17 and the flange portions 28 and 25, respectively. The head of the bolt 32 is supported in contact with the peripheral edge of the opening of the small-diameter bolt hole 35. In this state, the tip of the bolt 32 slightly protrudes outward from the large-diameter bolt hole 36. A nut 33 is fastened to the tip of the bolt 32 with an overload washer 40 interposed from the outside of the large-diameter bolt hole 36. Since the outer diameter of the overload washer 40 is smaller than the inner diameter of the large-diameter bolt hole 36, the overload washer 40 is received in the large-diameter bolt hole 36, and the end face of the overload washer 40 opposite to the nut 33 is Abut against the washer 39. An annular play space 41 is formed between the outer peripheral surface of the overload washer 40 and the inner peripheral surface of the large-diameter bolt hole 36 when viewed in the axial direction.

  The first disk element 17 assembled in this way is positioned with respect to both flange portions 28 and 25 by bolts 32 and nuts 33. In this state, the first disk element 17 can be bent and deformed along a trajectory R having a circular arc when viewed from the side centering on a predetermined position O on its own axis. In the following description, this position is referred to as “bending center O”. Even during this deformation, the length from the head of the bolt 32 to the nut 33 is not changed, but the bolt 32 and the nut 33 use the play space 41 with respect to the drive shaft side hub 16 and the spacer 18. The first disk element 17 can be smoothly bent and deformed by the relative displacement (see FIGS. 7 and 8). Even in this bent state, the first disk element 17 can transmit the rotation of the drive shaft side hub 16 to the spacer 17 by the tensile load transmitted to itself.

  The second disk element 19 is assembled in the same manner, and can be bent and deformed about the bending center O on its axis, and the rotation of the spacer 18 is transmitted to the driven shaft side hub 20 in this deformed state. can do.

  The flexible coupling structure 15 includes radial spherical bearings 42 and 42 incorporated inside the first and second disk elements 17 and 19. First, the bearing incorporated inside the first disk element 17 will be described.

  The radial spherical bearing 42 is a spherical plain bearing including an outer ring 43 having a spherical inner surface and an inner ring 44 housed inside the outer ring 43 in the radial direction and having a spherical outer surface. By adopting a general-purpose product that can be produced, it is possible to avoid an increase in costs required for the production and maintenance of the flexible coupling structure 15. The inner surface of the outer ring 43 and the outer surface of the inner ring 44 form a sliding surface that is close to each other, and the inner ring 44 is rotatable (slidable) along the spherical sliding surface with respect to the outer ring 43. . The radial spherical bearing 42 is an oil-free bearing that does not need to supply operating lubricant to these sliding surfaces. In this flexible coupling structure 15, since it is not necessary to supply the operating lubricating oil to the disk elements 17 and 19 which are the bending materials, the entire structure becomes an oilless type, and the cost and labor required for maintenance can be reduced. .

  The outer ring 43 has a cylindrical outer shape, and the radial spherical bearing 42 is mounted on the bearing support 45 by fitting the outer ring 43 into the cylindrical bearing support 45. The bearing support portion 45 is supported by a step portion formed on the inner peripheral side of the drive shaft side hub 16 and is positioned with respect to the drive shaft side hub 16. In this state, a plurality of bolts 46 are provided at the right end portion of the drive shaft 13. It is concluded with. As a result, the radial spherical bearing 42 is fixed to the drive shaft side hub 16 and assembled so that the position of the center of rotation (sliding center) thereof coincides with the drive shaft 13 and the shaft center 13A of the drive shaft side hub 16. Further, the radial spherical bearing 42 is incorporated in the flexible coupling 15 such that the position of the rotation center thereof coincides with the bending center O of the first disk element 17.

  The inner ring 44 has a cylindrical inner space, and a bearing support shaft 47 is mounted on the inner ring 44 so as to be fitted into the inner space. The bearing support shaft 47 protrudes from the center of the disc-shaped lid portion 48. The lid portion 48 has an annular rib 49 protruding from the surface opposite to the side from which the bearing support shaft 47 protrudes. By fitting the rib 49 to the left divided end portion 22, the left divided end portion is provided. 22 is positioned. In this state, the lid portion 48 is fastened to the left split end portion 22 with a plurality of bolts 50, whereby the bearing support shaft 47 is assembled such that its axis coincides with the axis 18 </ b> A of the left split end portion 22. . The bearing support shaft 47 may be formed separately from the lid portion 48 in advance, and may be integrated with the lid portion 48 through a joining process such as welding, or a single metal part is cut out. Then, the lid portion 48 may be integrally formed.

  When the bearing support shaft 47 is mounted on the inner ring 44, the drive shaft side hub 16 and the spacer 18 are coupled so that they can be inclined with each other when the inner ring 44 of the radial spherical bearing 42 slides on the outer ring 43. At this time, since the rotational center of the radial spherical bearing 42 coincides with the bending center O, the drive shaft side hub 16 and the spacer 18 are inclined with respect to the position of the bending center O, and the axial centers 13A, 18A of each other are inclined. Change the tilt angle.

  As described above, the position of the deflection center O of the first disk element 17 and the position of the rotational center of the radial spherical bearing 42 are coincident with each other, so that an unbalanced force due to unbalance is generated with respect to the spacer 18. Even so, the load is supported by the radial spherical bearing 42. As described above, since the lateral runout load during rotation can be supported, the lateral vibration of the spacer 18 does not occur. Further, since the rotational center of the radial spherical bearing 42 coincides with the bending center O of the first disk element 17, the first disk element 17 performs relative parallel displacement and tilt displacement while receiving an unbalanced force. It becomes possible.

  Since the spacer 18 is separated from the main body 21 and the left split end 22, the bearing support shaft 47 can be attached to the radial spherical bearing 42 without the main body 21 having a relatively long size and a large weight. . Then, after the assembly of both members 45 and 47 is completed, the left split end 22 can be connected to the main body 21 to integrate the long spacer 18, and the flexible coupling structure 15 can be assembled. Work labor can be reduced. Since the spacer 18 is hollow and its weight is small, the labor for assembling the flexible coupling structure 15 can be reduced, and the rotational starting torque of the prime mover can be reduced.

  When assembling the radial spherical bearing 42, the configuration is not limited to such a configuration, and the bearing support portion 45 may be fastened to the drive shaft side hub 16. Furthermore, the bearing support portion 45 may be fastened to the left split end portion 22 and the bearing support shaft 47 may be fastened to the drive shaft 13 or the drive shaft side hub 16 via the lid portion 48 (third embodiment). reference).

  In addition, a radial spherical bearing 42 is also incorporated in the inner side of the second disk element 19 in the same manner, thereby producing the same effects as described above. 1 shows a case where the bearing support portion 45 for mounting the radial spherical bearing 42 is fastened to the driven shaft 14 and the bearing support shaft 47 is fastened to the right split end portion 23 via the lid portion 48. Although illustrated, the bearing support portion 45 may be fastened to the driven shaft side hub 20. Further, the bearing support portion 45 may be fastened to the right split end portion 23 and the bearing support shaft 47 may be fastened to the driven shaft 14 or the driven shaft side hub 20 via the lid portion 48 (see the third embodiment). ).

  When the flexible coupling structure 15 having the above-described configuration is applied to an apparatus such as a marine thruster apparatus in which the prime mover and the driven machine are separated from each other in the horizontal direction and the prime mover is operated at a medium to high rotational speed. Therefore, even if the spacer 18 is long, the occurrence of lateral vibration is suppressed, and it is not necessary to support the spacer 18 with a dedicated intermediate bearing. In other words, since it is not necessary to provide such an intermediate bearing or to install a wall portion or a floor portion for fixing the intermediate bearing, it is possible to reduce costs, man-hours and time in manufacturing a device such as a marine thruster device. In addition, the space reserved for installing the wall and floor can be used effectively for other purposes.

[Second Embodiment]
FIG. 3 is a front view of a marine thruster apparatus 51 including a vertical shaft type flexible coupling structure 65 according to the second embodiment of the present invention. In addition, about the structure similar to the said embodiment, the same code | symbol is attached | subjected and detailed description is abbreviate | omitted.

  The marine thruster device 51 shown in FIG. 3 includes a prime mover 52 such as an electric motor or a diesel engine, a thruster 53 that is a driven machine, and a flexible coupling structure 65 that is interposed between the prime mover 52 and the thruster 53. Has been. The prime mover 52 is disposed vertically upward with respect to the thruster 53, and the flexible coupling structure 65 is disposed so as to extend in a substantially vertical direction between the prime mover 51 and the thruster 53. According to this marine thruster device 51, when the prime mover 52 is operated, the drive shaft 13 that is rotatably connected to the prime mover 52 is rotated, and the rotation is transmitted to the driven shaft 14 via the flexible coupling structure 65. The The driven shaft 14 is rotatably connected to the thruster 53 and functions as an input shaft of the thruster 53, and the propeller 54 of the thruster 53 is rotationally driven based on the rotation of the driven shaft 14. Since this flexible coupling structure 65 is also configured to suppress the occurrence of vibration in the same manner as in the first embodiment, this marine thruster device 51 can also reduce the cost, man-hours and time required for its production. This makes it possible to effectively use the previously reserved space.

  4 is a cross-sectional view of the flexible coupling structure 65 shown in FIG. The flexible coupling structure 65 is disposed with the drive shaft 13 and the driven shaft 14 so that the axial direction is substantially vertical, and the drive shaft side hub 16, the first disk element 17, the spacer 18, 2 The disk element 19 and the driven shaft side hub 20 are provided, and the rotation of the drive shaft 13 is transmitted in this order. That is, the spacer 18 of the present embodiment also functions as a driven shaft side rotating shaft member for the driving shaft side hub 16 and functions as a driving shaft side rotating shaft member for the driven shaft side hub 20. It becomes. The spacer 18 is also integrated with the main body portion 21 by fastening two divided end portions with a plurality of joint bolts such as a reamer bolt 24. However, the spacer 18 is divided into two portions based on whether the power transmission is upstream. Of the ends, the upper divided end portion is denoted by the same reference numeral 22 as the left divided end portion of the first embodiment, and the lower divided end portion is denoted by the same reference numeral 23 as the right divided end portion of the first embodiment. Is attached.

  A radial spherical bearing 42 is incorporated in the first disk element 17 in the same manner as in the first embodiment. The second disk element 19 is arranged vertically downward with respect to the first disk element 17, and a thrust spherical bearing 66 is incorporated in the inside thereof together with the radial spherical bearing 42.

  The vertically lower radial spherical bearing 42 is mounted by fitting the outer ring 43 inside a cylindrical bearing support portion 67, and the bearing support portion 67 is attached to the upper end portion of the driven shaft 14 with a plurality of bolts 68. It is concluded with. A bearing support shaft 69 is mounted on the inner ring 44 of the radial spherical bearing 42, and the bearing support shaft 69 is fastened to the lower divided end portion 23 with a plurality of bolts 71 via a lid 70.

  The thrust spherical bearing 66 is a spherical plain bearing including an outer ring 72 having a spherical inner surface, and an inner ring 73 disposed on the axially upper side and the radial inner side with respect to the outer ring 72 and having a spherical outer surface. In addition, the use of a spherical plain bearing, which is a general-purpose product that can be mass-produced, can avoid an increase in costs required for the production and maintenance of the flexible coupling structure 65. The inner surface of the outer ring 72 and the outer surface of the inner ring 73 form a sliding surface that is close to each other and the inner ring 73 is rotatable (slidable) along the spherical sliding surface with respect to the outer ring 72. Further, the thrust spherical bearing 66 is an oil-free bearing, which can reduce the cost and labor required for maintenance and management of the flexible coupling structure 65.

  In the present embodiment, a bearing support portion 67 for mounting the radial spherical bearing 42 and the thrust spherical bearing 66 is shared between the two bearings 42 and 66, and the thrust spherical bearing 66 is provided inside the bearing support portion 67. The radial spherical bearing 42 is arranged on the back side (here, the lower side) approaching the end surface of the driven shaft 14. Specifically, the outer shape of the outer ring 72 of the thrust spherical bearing 66 is cylindrical, and the thrust spherical bearing 66 is mounted on the bearing support 67 by fitting the outer ring 72 into the bearing support 67. Yes. Thereby, the thrust spherical bearing 66 is assembled in the flexible coupling structure 65 so that the position of the rotation center (sliding center) coincides with the axis 14A of the driven shaft 14. A projection 74 protruding radially inward is formed on the inner surface of the bearing support portion 67 on the back side, and the outer ring 72 of the thrust spherical bearing 66 is an upper portion of the projection 74 that faces the internal space of the bearing support portion 67. It is supported on the end face. The outer ring 72 is thus supported by the protrusion 74, whereby the thrust spherical bearing 66 is positioned with respect to the bearing support portion 67 in the axial direction.

  The inner ring 73 of the thrust spherical bearing 66 is disposed above the outer ring 72, and the inner ring 44 of the radial spherical bearing 42 is supported on the upper side of the inner ring 73. Accordingly, the radial spherical bearing 42 is positioned with respect to the bearing support portion 67 in the axial direction via the thrust spherical bearing 66. Thus, the inner ring 44 of the radial spherical bearing 42 and the inner ring 73 of the thrust spherical bearing 66 are arranged side by side in the axial direction. The bearing support shaft 69 is mounted on the inner ring 44 of the radial spherical bearing 42 from the upper side, which is the side approaching the lid part 70, and its tip is fitted in the inner space of the inner ring 73 of the thrust spherical bearing 66. Here, the inner diameter of the inner ring 73 of the thrust spherical bearing 66 is smaller than the inner diameter of the inner ring 44 of the radial spherical bearing 42, and the bearing support shaft 69 is formed in a stepped cylindrical shape having a smaller outer diameter on the tip side. The step portion is supported on the upper surface of the inner ring 73 of the thrust spherical bearing 66. As described above, in this embodiment, the bearing support shaft 69 supported by the radial spherical bearing 42 and the thrust spherical bearing 66 is shared between the two bearings 42 and 66.

  According to the above configuration, the thrust spherical bearing portion 66 and the radial spherical bearing portion 42 are assembled in the order from the rear side approaching the end surface of the driven shaft 14 in the bearing support portion 67 to the front opening side. The bearings 66 and 42 can be unitized in the bearing support portion 67. Therefore, in a state where the two bearings 66 and 42 are assembled in the bearing support portion 67, the two bearings 66 and 42 are fixed to the bearing support shaft 69 fixed to the spacer 18 side via the lid portion 70. Can be easily attached and detached. That is, it is not necessary to attach and detach the two bearings 66 and 42 with respect to the bearing support portion 67 and the bearing support shaft 69 one by one.

  The thrust spherical bearing 66 can change the inclination angle of each of the shaft centers 14A and 18A with the intersection point when the shaft centers 14A and 18A of the driven shaft 14 and the spacer 18 are inclined as the rotation center (sliding center). In other words, since the center of rotation coincides with the deflection center O of the second disk element 19, the tilt angle of the shaft centers 14A and 18A of the driven shaft 14 and the spacer 18 is changed by the thrust spherical bearing portion 66. However, a thrust load based on the weight of the spacer 18 can be supported.

  Although the weight of the spacer 18 is applied to the thrust spherical bearing 66, the weight is supported by the thruster 53 (see FIG. 3). Since the load of the spacer 18 is thus held by the thrust spherical bearing 66 disposed downstream of the power transmission and vertically below, the load of the spacer 18 is applied to the prime mover 52 (see FIG. 3). The standard design product can be selected and used for the prime mover 52.

  Specifically, for example, when the flexible coupling structure 65 is applied to a marine thruster device 51 (see FIG. 3) whose transmission horsepower is 4500 kw class, the size and weight of the spacer 18 are considerably increased (for example, outer diameter: About 400 mm, shaft length: about 5500 mm, weight: about 800 kg). Therefore, when the thrust spherical bearing 66 is assembled inside the first disk element 17 interposed between the drive shaft side hub 16 and the spacer 18, the weight of the thrust spherical bearing 66 must be supported on the prime mover 52 side. On the other hand, the standard design product of the prime mover 52 is not normally provided with a structure for supporting the specially added weight, and when the thrust spherical bearing 66 is incorporated as described above, the prime mover is provided. 52 needs to be changed. In this embodiment, since it is set as the structure which does not require the specification change of such a motor | power_engine 52, it can avoid that the expense required for arrangement of the motor | power_engine 52 increases. As described above, according to this embodiment, it is possible to provide a self-load support type / self-contained flexible coupling structure that receives a load on the thruster 53 side and does not affect the prime mover 52 side. The thruster 53 side has a higher degree of design freedom than the prime mover 52 side, and a structure for holding a load in the thrust direction can be easily arranged in this portion.

  FIG. 5 is a partially enlarged view of FIG. A position adjusting shim 75 is inserted between the lower end portion of the inner ring 44 of the radial spherical bearing 42 and the upper end portion of the inner ring 73 of the thrust spherical bearing 66. Further, the bearing support shaft 69 is formed with a shoulder portion 76 that protrudes radially outward from the outer peripheral surface at the base end portion (here, the upper end portion) that is closer to the lid portion 70. It is arranged on the upper side with respect to the radial spherical bearing 42. A position adjusting shim 77 is inserted between the shoulder 76 and the upper end of the inner ring 43 of the radial spherical bearing 42. A position adjusting shim 78 is inserted between the upper surface of the protrusion 74 of the bearing support 67 and the lower end of the outer ring 72 of the thrust spherical bearing 66.

  A shim 75 interposed between the radial spherical bearing 42 and the thrust spherical bearing 66 relatively adjusts and matches the center positions of both the bearings 42 and 66. This is the first adjustment work when assembling both the bearings 42 and 66. Next, shims 77 and 78 are used in the second adjustment operation. That is, the shims 77 and 78 are used so that the center position thereof coincides with the position of the bending center O of the second disk element 19 in a state where the two bearings 42 and 66 having the same rotation center are combined and unitized. In this way, both bearings 42 and 66 are assembled. By providing the shims 75, 77, 78 in this way, the rotational centers of the thrust spherical bearing 66 and the radial spherical bearing 42 and the position of the bending center O of the second disk element 19 are finely adjusted and easily matched. This adjustment work can be performed in a short time.

  Further, a gap 79 is formed between the outer peripheral surface of the outer ring 73 of the thrust spherical bearing 66 and the inner peripheral surface of the bearing support portion 67. By forming the gap 79, the unbalanced force is supported by the radial spherical bearing 42, and is not configured to be supported by the thrust spherical bearing 66. Therefore, the thrust spherical bearing 66 receives only the weight of the spacer 18 of the flexible coupling structure 65.

  In other embodiments to be described later, when a flexible coupling structure provided with a thrust spherical bearing is shown, it is assumed that the same configuration as that shown in FIG. 5 is adopted, and description and illustration regarding the configuration are omitted. To do.

  Next, with reference to FIG. 6, the operation | work which confirms whether the assembly | attachment of the flexible coupling structure 65 is appropriate is demonstrated. This “confirms whether or not the assembly is appropriate” means that the rotational center of the radial spherical bearing 42 is changed even if the inclination angles of the axis 14A of the driven shaft 14 and the axis 18A of the spacer 18 are changed. In this case, it is confirmed whether or not the respective positions of the rotational center of the thrust spherical bearing 66 and the bending center of the second disk element 19 are in agreement with each other. If the deflection center of the second disk element 19 and the rotation center of the bearings 42 and 66 do not coincide with each other, there is a possibility that the bearings 42 and 66 may be seized, etc. There is also.

  The confirmation operation and the adjustment operation for making the respective center positions coincide with each other with the driven shaft side hub 20, the second disk element 19, the bearings 42 and 66, and the spacer 18 in the assembled state, This can be done by relatively rocking. For example, if the confirmation work and the adjustment work are performed at the stage where the main body 21 and the divided end portions 22 and 23 are connected as shown in FIG. 4, it is necessary to swing the entire spacer 18 having a large size and weight. Therefore, a great deal of labor and time are required for the confirmation work and the adjustment work.

  On the other hand, as shown in FIG. 6, the main body 21 does not exist before the divided end 23 of the spacer 18 is connected to the main body 21, and the driven shaft side hub 20 and the bearings 42, 66 A lightweight and compact assembly including only the second disk element 19 and the lower divided end 23 is formed. In this state, after the bearings 42 and 66 are assembled, the lower divided end portion 23 can be easily swung by hand, and the rotation centers of the bearings 42 and 66 and the bending centers of the second disk elements 19 It can be confirmed whether or not. In addition, since the work can be easily performed by hand as described above, is the flexible coupling structure 65 properly assembled based on the feeling transmitted when the operator moves the lower divided end portion 23 or the like? It is possible to easily determine whether or not. In this way, the confirmation work and adjustment work can be performed reliably and in a short time. It should be noted that such confirmation work and adjustment work can be performed in the same manner in the first disk element 17 and the upper radial spherical bearing 42 in a similar manner. In addition, the above-described burn-in or the like can be prevented in advance, and the lifetime of the flexible coupling structure 65 can be prevented from being shortened.

  Next, the operation of the flexible coupling structure 65 when a relative displacement occurs between the drive shaft 13 and the driven shaft 14 will be described with reference to FIGS. 7 and 8.

  7 is a cross-sectional view showing a state where the driven shaft 14 connected to the flexible coupling structure 65 shown in FIG. At this time, the shaft center 13A of the drive shaft 13 and the shaft center 14A of the driven shaft 14 are parallel to the vertical axis S, but are separated from each other by a predetermined distance δ. Even in this case, each of the disk elements 17 and 19 is bent, and the spacer 18 is inclined with respect to the vertical axis S by a predetermined angle θ1 based on the distance δ and its own axial length. Even in this bent state, the rotation of the drive shaft side hub 16 is transmitted to the spacer 18 via the first disk element 17, and the rotation of the spacer 18 is transmitted to the driven shaft side hub 20 via the second disk element 19. The Therefore, the rotation generated by the prime mover 52 (see FIG. 3) is smoothly transmitted to the thruster 53 (see FIG. 3) via the flexible coupling structure 65.

  FIG. 8 is a cross-sectional view showing a state where the drive shaft 13 connected to the flexible coupling structure 65 shown in FIG. 4 is inclined and displaced (angular displacement) with respect to the driven shaft 14. The axis 18A of the spacer 18 is parallel to the vertical axis S, the axis 13A of the drive shaft 13 is inclined by a predetermined angle θ2 with respect to the vertical axis S, and the axis 14A of the driven shaft 14 is aligned with the vertical axis S. It is inclined with respect to the predetermined angle θ3. Even in this case, the disk elements 17 and 19 are bent to absorb the displacements of the angles θ2 and θ3, respectively. Even in this bent state, the rotation of the drive shaft side hub 16 is transmitted to the spacer 18 via the first disk element 17, and the rotation of the spacer 18 is transmitted to the driven shaft side hub 20 via the second disk element 19. The Therefore, the rotation generated by the prime mover 52 (see FIG. 3) is smoothly transmitted to the thruster 53 (see FIG. 3) via the flexible coupling structure 65.

[Third Embodiment]
FIG. 9 is a sectional view of a vertical axis flexible coupling structure 85 according to a third embodiment of the present invention. Here, it demonstrates centering on difference with 2nd Embodiment shown in FIG. A radial spherical bearing 42 is incorporated inside the first disk element 17 of the flexible coupling structure 85 shown in FIG. A bearing support 47 for mounting the radial spherical bearing 42 is fixed to the upper divided end 22 constituting the spacer 18, and a bearing support shaft 47 supported by the radial spherical bearing 42 is interposed via a lid 48. And fastened to the lower end of the drive shaft 13 and fixed to the drive shaft-side hub 16. Referring to FIG. 4 as well, it is possible to appropriately select whether the bearing support portion 45 and the bearing support shaft 47 are fixed to the drive shaft side hub 16 or the spacer 18, respectively.

  In addition, a radial spherical bearing 42 and a thrust spherical bearing 66 are incorporated inside the second disk element 19. A bearing support portion 86 for mounting these bearings 42 and 66 is fixed to the lower divided end portion 23 forming the spacer 18. A bearing support shaft 87 supported by the bearings 42 and 66 is fixed to the driven shaft 14 via a lid portion 88. Each of the bearings 42 and 66 is attached to the bearing support portion 86 so that the thrust spherical bearing 66 is disposed on the back side (here, the upper side) with respect to the radial spherical bearing 42.

  A protrusion 89 protruding radially inward is formed at the lower end of the lower split end 23, and a circular hole 90 surrounded by the protrusion 89 is formed. A flange portion 91 is formed on the upper end portion of the bearing support portion 86 so as to protrude radially outward from the outer peripheral surface thereof. The bearing support portion 86 is positioned with respect to the lower divided end portion 23 by receiving the upper end portion thereof in the hole 90 inside the projection 89 and supporting the flange portion 91 on the lower surface of the projection 89. A plurality of bolts 92 are fastened to the lower split end 23. The lid portion 88 is supported by a step portion formed on the inner peripheral side of the driven shaft side hub 20 and is positioned with respect to the driven shaft side hub 20. In this state, the lid portion 88 is fastened to the upper end portion of the driven shaft 14 with a plurality of bolts 93. Has been.

  Thus, also in this embodiment, the bearing support portion 86 and the bearing support shaft 87 are shared between the radial spherical bearing 42 and the thrust spherical bearing 66. Therefore, if the retaining ring 94 is positioned and held further below the radial spherical bearing 42 arranged on the lower side in the vertical direction, the two bearings 42 and 66 can be unitized in the bearing support portion 86.

[Fourth Embodiment]
FIG. 10 is a cross-sectional view of a horizontal axis type flexible coupling structure 95 according to a fourth embodiment of the present invention. In contrast to the first embodiment shown in FIG. 1, in the flexible coupling structure 95 shown in FIG. 10, the radial spherical bearing 96 incorporated in each disk element 17 and 19 is a spherical rolling bearing. Spherical rolling bearings are also general-purpose products that can be mass-produced, and by adopting them, it is possible to avoid an increase in costs required for the production and maintenance of the flexible coupling structure 95. Even if the spherical plain bearing is replaced with a spherical rolling bearing, the lateral runout load can be supported in the same manner as in the above embodiment.

[Fifth Embodiment]
FIG. 11 is a cross-sectional view of a vertical shaft type flexible coupling structure 105 according to a fifth embodiment of the present invention. In contrast to the second embodiment shown in FIG. 4, in the flexible coupling structure 105 shown in FIG. 11, the radial spherical bearing 106 incorporated inside the first disk element 17 and the inner side of the second disk element 19. The radial spherical bearing 106 and the thrust spherical bearing 107 incorporated in the above are respectively spherical rolling bearings. For this reason, it is possible to support a lateral runout load and a load in the thrust direction, and to avoid an increase in costs required for manufacturing and maintenance inspection of the flexible coupling structure 105.

[Sixth Embodiment]
FIG. 12 is a perspective view partially showing the appearance of the flexible coupling structure 115 according to the sixth embodiment of the present invention, and FIG. 13 is a cross-sectional view of the flexible coupling structure 115 shown in FIG. Here, a case where the flexible coupling structure 115 of the present embodiment is a horizontal axis type will be described, but a vertical axis type can also be used.

  In FIG. 12, a drive shaft side hub 116 connected to a drive shaft (not shown) in the flexible coupling structure 115, a first leaf spring 117, and a left divided end portion 122 constituting the spacer 118 are shown. It is shown. In FIG. 13, the main body 121 and the right split end 123 constituting the spacer 118 of the flexible coupling structure 115, the second leaf spring 119, and the driven shaft side hub 120 connected to the driven shaft 14 are shown. It is shown. As shown in FIG. 13, the spacer 118 is connected to each other by a main body 121, a right split end 123, and a reamer bolt 124. Although not shown, the main body 121 can be connected to the left split end 122 (see FIG. 12) in the same manner. It has become.

  As shown in FIG. 12, the first leaf spring 117 is a so-called lattice-shaped leaf spring made of metal, and is provided so as to span between the drive shaft side hub 116 and the left divided end portion 122. As continuous in the circumferential direction. The first leaf spring 117 is connected to both the drive shaft side hub 116 and the left split end 122, and can be bent and deformed in the same manner as the first disk element 17 of the above embodiment. Even in this bent state, the rotation of the drive shaft side hub 116 is transmitted to the spacer 118. A cover member 131 is provided to cover the outer peripheral side of the first leaf spring 117. In FIG. 12, the cover 131 is partially broken to show the appearance of the first leaf spring 117. The shape and material of the second leaf spring 119 are the same as those of the first leaf spring 117 shown in FIG. 12, and the combination of the second leaf spring 119 with the right split end 123 and the driven shaft side hub 120 is also shown in FIG. This is the same as the combination of the first leaf spring 117, the left split end 122 and the drive shaft side hub 116 shown in FIG. The second leaf spring 119 can be bent and deformed around its bending center O in the same manner as the second disk element 19 of the above embodiment. Even in this bent state, the rotation of the spacer 118 is driven. It is transmitted to the shaft side hub 120. A cover member 131 is provided to cover the outer peripheral side of the second leaf spring 119.

  As shown in FIGS. 12 and 13, the cover member 131 is integrated by fastening a left half 132 and a right half 133 separable in the axial direction with a plurality of bolts 134. Referring to FIG. 12, the left half 132 of the cover member 131 that covers the first leaf spring 117 is formed on the outer peripheral surface of the drive shaft side hub 116, and the right half 133 is formed on the left split end 122. It is engaged with the outer peripheral surface. Referring to FIG. 13, the left half 132 of the cover member 131 that covers the second leaf spring 119 engages with the outer peripheral surface of the right split end 123, and the right half 132 engages with the outer peripheral surface of the right split end 123. Is engaged.

  As shown in FIG. 13, a radial spherical bearing 42 is incorporated inside the second leaf spring 119. A bearing support portion 45 for mounting the radial spherical bearing 42 is supported by a step portion formed on the inner peripheral side of the driven shaft side hub 120 and positioned with respect to the driven shaft side hub 120. The bolt 46 is fastened to the left end portion of the driven shaft 14. A bearing support shaft 47 supported by the radial spherical bearing 42 protrudes from a disc-shaped lid portion 48, and the lid portion 48 is fitted to the right side divided end portion 123, whereby the right side divided end portion 123. In this state, a plurality of bolts 50 are fastened to the right split end portion 123. The center of rotation of the radial spherical bearing 42 is coincident with the center of deflection of the second leaf spring 119, thereby providing the same effects as those of the above embodiments. Although not shown in the drawing, a radial spherical bearing 42 is also incorporated in the first leaf spring 117, and the same effect is obtained.

  In the illustration of FIG. 13, a spherical plain bearing is adopted as the radial spherical bearing 42 incorporated in the flexible coupling structure 115, but a spherical rolling bearing may be adopted instead of this, and there is no lubrication. It is preferable to employ a bearing. Alternatively, the bearing support shaft 47 may be fixed to the driven shaft side hub 120 by being fixed to the right split end portion 123. Here, the case of adopting the horizontal axis type is illustrated, but when the vertical axis type is adopted, the thrust spherical bearing is used in the same manner as in the second embodiment shown in FIG. 4 and the fifth embodiment shown in FIG. Just include it.

[Seventh Embodiment]
FIG. 14 is a perspective view partially showing an appearance of a flexible coupling structure 165 according to the seventh embodiment of the present invention, and FIG. 15 is a cross-sectional view of the flexible coupling structure 165 shown in FIG. Here, the case where the flexible coupling structure 165 of the present embodiment is a horizontal axis type will be described, but a vertical axis type can also be used.

  FIG. 14 shows a drive shaft side hub 166 to which a drive shaft (not shown) of the flexible coupling structure 165 is connected, a first rubber 167, and a left divided end portion 172 constituting the spacer 168. Has been. FIG. 15 shows the main body 171 and the right split end 173 constituting the spacer 168 in the flexible coupling structure 165, the second rubber 169, and the driven shaft side hub 170 connected to the driven shaft 14. Has been. As shown in FIG. 15, the spacer 168 is connected to each other by a main body 171, a right split end 173, and a reamer bolt 174. Although not shown, the main body 171 can be connected to the left split end 172 (see FIG. 14) in the same manner. It has become. The configuration from the drive shaft side hub 166 to the left split end portion 172 shown in FIG. 14 and the configuration from the right split end portion 173 to the driven shaft side hub 170 shown in cross section in FIG. 15 are symmetrical with respect to the axial direction. Although arranged, the mutual structure is the same. In the following, with reference to FIG. 15, description will be made by paying attention to a portion on the side where the second rubber 169 is arranged on behalf of these two portions.

  As shown in FIG. 15, the 2nd rubber | gum 169 is formed in the tire shape, and the cross-sectional shape is U-shaped. The left edge 169 a of the second rubber 169 is locked to the outer side surface (here, the left side surface) of the flange portion 176 of the right split end 173, and the right edge 169 b of the second rubber 169 is fixed to the driven shaft side hub 170. The flange portion 180 is locked to the outer side surface (here, the right side surface). Thereby, the second rubber 169 is interposed between the spacer 168 and the driven shaft side hub 170. An annular fixing plate 181 is fastened to the flange portion of the right split end portion from the outside by a plurality of bolts 182, whereby the left edge 169 a of the second rubber 169 is interposed between the flange portion 176 and the fixing plate 181. Firmly held. Similarly, an annular fixing plate 183 is fastened to the flange portion 180 of the driven shaft side hub 170 from the outside by a plurality of bolts 184, whereby the right edge 169 b of the second rubber 169 is flanged. It is firmly held between the portion 180 and the fixed plate 183. Each of the fixing plates 181 and 183 and the flange portions 176 and 180 is formed with an annular receiving groove 185 for receiving the edge portions 169a and 169b at the portion holding the second rubber 169. By fastening with a bolt in a state where the edge is received in the receiving groove 185, the bending center O of the second rubber is set at a predetermined position.

  A radial spherical bearing 42 is incorporated inside the second rubber 169. The bearing support portion 45 for mounting the radial spherical bearing 42 is supported by a step portion formed on the inner peripheral side of the driven shaft side hub 170 and is positioned with respect to the driven shaft side hub 170. The bolt 46 is fastened to the left end portion of the driven shaft 14. A bearing support shaft 47 supported by the radial spherical bearing 42 protrudes from a disc-shaped lid portion 48, and the lid portion 48 is fitted to the right side divided end portion 173, whereby the right side divided end portion 173. And is fastened to the right split end 173 with a plurality of bolts 50 in this state. The center of rotation of the radial spherical bearing 42 coincides with the center of deflection of the second rubber 169, and the same effects as those of the above-described embodiments are thereby obtained. Although not shown in the drawing, a radial spherical bearing is also incorporated in the first rubber 167 (see FIG. 14), and the same effect is obtained.

  In the example of FIG. 15, a spherical plain bearing is adopted as the radial spherical bearing 42 incorporated in the flexible coupling structure 165, but a spherical rolling bearing may be adopted instead of this, and there is no oil supply. It is preferable to employ a bearing. Alternatively, the bearing support shaft 47 may be fixed to the driven shaft side hub 170 by being fixed to the right split end portion 173. Here, the case of adopting the horizontal axis type is illustrated, but when the vertical axis type is adopted, the thrust spherical bearing is used in the same manner as in the second embodiment shown in FIG. 4 and the fifth embodiment shown in FIG. Just include it.

  Although the embodiment of the present invention has been described so far, the embodiment of the present invention is not limited to the above-described configuration and can be appropriately changed within the scope of the invention.

  For example, in each of the vertical shaft type flexible coupling structures, the thrust spherical bearing is incorporated inside the second disk element on the vertically lower side, but the spacer is incorporated inside the first disk element on the vertically upper side. It is good also as a structure which suspends and supports by a thrust spherical bearing. Note that it is possible to appropriately select whether the bearing support portion for mounting the two bearings and the bearing support shaft supported by these bearings are fixed to the drive shaft side hub or the spacer.

  Further, in each of the vertical shaft type flexible coupling structures, when the load capacity of the radial spherical bearing is increased, a load in the thrust direction can be supported by the radial spherical bearing. As a result, the load capacity of the thrust spherical bearing can be reduced, and the thrust spherical bearing can be omitted.

  Moreover, in each embodiment, although the case where the bearing integrated in the flexible coupling structure was unified in either one of a spherical plain bearing and a spherical rolling bearing was illustrated, a spherical plain bearing and a spherical rolling bearing were mixed. Also good.

  The flexible coupling structure is not limited to the one provided with the two bending members with the spacer interposed therebetween, and the bending member may be interposed between the drive shaft side hub and the driven shaft side hub. In this case, one radial spherical bearing may be incorporated in the inside of this single flexible member, and one more thrust spherical bearing may be incorporated as necessary.

  The flexible coupling structure according to the present invention is not limited to the marine thruster device as shown in FIG. 3, and can be suitably applied to other uses.

  As described above, the flexible coupling structure according to the present invention has an excellent effect of suppressing the occurrence of vibration even when the entire length is long, and the installation distance between the prime mover and the thruster tends to be large. It is beneficial to apply to a marine thruster device in which the prime mover can be operated at medium and high speeds, and it is also suitably applied to other machines, instruments, and devices that require a structure for transmitting rotation between two shafts. be able to.

It is sectional drawing of the horizontal axis type flexible coupling structure which concerns on 1st Embodiment of this invention. It is a disassembled perspective view of the flexible coupling structure shown in FIG. It is a front view of the marine thruster apparatus to which the vertical axis type flexible coupling structure which concerns on 2nd Embodiment of this invention is applied. It is sectional drawing of the flexible coupling structure shown in FIG. It is the elements on larger scale of FIG. It is sectional drawing explaining the operation | work for confirming the assembly | attachment of the flexible coupling structure shown in FIG. FIG. 5 is a cross-sectional view showing a state in which the driven shaft is displaced in parallel relative to the drive shaft in the flexible coupling structure shown in FIG. 4. FIG. 5 is a cross-sectional view showing a state where the drive shaft and the driven shaft are angularly displaced in the flexible coupling structure shown in FIG. 4. It is sectional drawing of the flexible coupling structure of the vertical axis type which concerns on 3rd Embodiment of this invention. It is sectional drawing of the horizontal axis type flexible coupling structure which concerns on 4th Embodiment of this invention. It is sectional drawing of the vertical axis type flexible coupling structure which concerns on 5th Embodiment of this invention. It is a perspective view which shows partially the external appearance of the flexible coupling structure which concerns on 6th Embodiment of this invention. It is a fragmentary sectional view of the flexible coupling structure shown in FIG. It is a perspective view which shows partially the external appearance of the flexible coupling structure which concerns on 7th Embodiment of this invention. It is a fragmentary sectional view of the flexible coupling structure shown in FIG. It is sectional drawing of the metal spring type flexible coupling shown as an example of the conventional flexible coupling. It is a front view of the conventional marine thruster apparatus to which the flexible coupling shown in FIG. 16 is applied.

Explanation of symbols

13 Drive shaft 14 Driven shaft 15 Horizontal shaft type flexible coupling structure 16 Drive shaft side hub (rotary shaft member on the drive shaft side)
17 First disc element (first deflecting material)
18 Spacer 19 Second disk element (second deflecting material)
20 Driven shaft side hub (Rotating shaft member on the driven shaft side)
DESCRIPTION OF SYMBOLS 21 Main body parts 22 and 23 Division | segmentation edge part 24 Reamer bolt 31 Disc shaped leaf | plate spring 42 Radial spherical bearing 45 Bearing support part 47 Bearing support shaft 51 Marine thruster apparatus 52 Engine 53 Thruster 65 Vertical axis type flexible coupling structure 66 Thrust spherical bearing 67 Bearing support portion 69 Bearing support shaft 85 Vertical shaft type flexible coupling structure 86 Bearing support portion 87 Bearing support shaft 95 Horizontal shaft type flexible coupling structure 96 Radial spherical bearing 105 Vertical shaft type flexible coupling structure 106 Radial spherical bearing 107 Thrust spherical bearing 115 Horizontal shaft type flexible coupling structure 116 Drive shaft side hub (rotary shaft member on the drive shaft side)
117 1st lattice-shaped leaf | plate spring (1st bending material)
118 Spacer 119 Second Lattice Plate Spring (Second Deflection Material)
120 Driven shaft side hub (Rotating shaft member on the driven shaft side)
121 Body 122, 123 Split end 124 Reamer bolt 165 Horizontal shaft type flexible coupling structure 166 Drive shaft side hub (drive shaft side rotating shaft member)
167 First tire-shaped rubber (first flexible material)
168 Spacer 169 Second tire-shaped rubber (second flexible material)
170 Driven shaft side hub (Rotating shaft member on the driven shaft side)
171 Body 172, 173 Split end 174 Reamer bolt

Claims (14)

  In a metal spring-type or rubber-type flexible coupling structure that connects a drive shaft and a driven shaft, a bending made of a metal spring or rubber is interposed between the rotary shaft member on the drive shaft side and the rotary shaft member on the driven shaft side. A radial spherical bearing is incorporated at the position of the center of bending of the material so that the center of rotation is positioned, and the rotating shaft member on the driving shaft side or the rotating shaft member on the driven shaft side is supported by the radial spherical bearing, and the bending is performed. A flexible coupling structure characterized in that the rotating shaft member on the drive shaft side can be inclined relative to the rotating shaft member on the driven shaft side with respect to the center.   A bearing support for mounting the radial spherical bearing is fixed to one of the rotary shaft member on the drive shaft side and the rotary shaft member on the driven shaft side, and is supported by the radial spherical bearing. The flexible coupling structure according to claim 1, wherein the shaft is fixed to the other side.   The rotary shaft member on the drive shaft side or the rotary shaft member on the driven shaft side includes a main body portion and a split end portion that is combined with the bending material and fixed to the bearing support portion or the bearing support shaft. 3. The flexible coupling structure according to claim 1, wherein the flexible coupling structure is integrated by fastening the main body portion and the split end portion with a joint bolt including a reamer bolt.   The flexible coupling structure according to any one of claims 1 to 3, wherein the radial spherical bearing is a spherical plain bearing or a spherical rolling bearing.   The metal spring type or rubber type flexible coupling structure is a vertical shaft type, and the radial spherical bearing has a large load capacity, and can support a load in a radial direction and a thrust direction. The flexible coupling structure according to any one of 1 to 4.   The metal spring-type or rubber-type flexible coupling structure is a vertical shaft type, and a thrust spherical bearing is incorporated in the position of the bending center of the bending material so that the rotation center is positioned, and the rotating shaft member on the drive shaft side 6. The flexible coupling structure according to claim 1, wherein the rotating shaft member on the driven shaft side is supported by the radial spherical bearing and the thrust spherical bearing.   A bearing support for mounting the thrust spherical bearing is fixed to one of the rotating shaft member on the drive shaft side and the rotating shaft member on the driven shaft side, and is supported by the thrust spherical bearing. The flexible coupling structure according to claim 6, wherein the support shaft is fixed to the other side.   The radial spherical bearing is mounted on a bearing support portion for mounting the thrust spherical bearing, and a tip end portion of a bearing support shaft supported by the radial spherical bearing is supported by the thrust spherical bearing. The flexible coupling structure according to claim 7. A spacer interposed between the rotary shaft member on the drive shaft side and the rotary shaft member on the driven shaft side, the spacer being connected to the rotary shaft member on the driven shaft side with respect to the rotary shaft member on the drive shaft side; None, with respect to the rotating shaft member on the driven shaft side, there is no rotating shaft member on the drive shaft side,
The first flexible member is interposed between the rotary shaft member on the drive shaft side and the spacer, and the first flexible member is incorporated so that the rotational center is located at the position of the deflection center of the first flexible member. The radial spherical bearing is supported by the rotary shaft member or the spacer on the drive shaft side,
The second bending material is interposed between the spacer and the rotating shaft member on the driven shaft side, and the second bending material is incorporated so that the rotation center is located at the position of the bending center of the second bending material. The radial spherical bearing is supported by the rotating shaft member on the spacer or the driven shaft side;
9. The thrust spherical bearing according to claim 6, wherein the thrust spherical bearing is incorporated into any one of the first radial spherical bearing and the second radial spherical bearing. 10. Flexible coupling structure.   The flexible coupling structure according to claim 6, wherein the thrust spherical bearing is a spherical sliding bearing or a spherical rolling bearing.   The flexible coupling structure according to claim 1, wherein the flexible member is a disk-shaped leaf spring.   The flexible coupling structure according to claim 1, wherein the flexible member is a lattice-shaped leaf spring.   The flexible coupling structure according to claim 1, wherein the flexible member is a tire-shaped rubber.   A flexible coupling structure according to claim 1 is provided, and rotation of the drive shaft provided in the prime mover is transmitted to the driven shaft provided in the thruster via the flexible coupling structure. A marine thruster device comprising the marine thruster.

Images